Friction device



Aug. 30, 193@ .1. L. MossEY 2,950,783

FRCTION DEVICE Filed Nov. 9, 955 3 Sheets-Sheet l iff/i4 IN VEN TOR.

Allg' 30, 1960 J. L. MossEY 2,950,783

FRICTION DEVICE Filed Nov. 9, 1955 3 Sheets-Sheet 2 IN V EN TOR.

Aug. 30, 1960 J. l.. Mossa# 950,783

FRICTION DEVICE vFiled NOV. 9, 1955 3 Smets-Sheet 3 INVENTOR.

United@ safes enen ofi 2,950,783 FRICTION DEVICE Joseph L. Mossey, South Bend, Ind., assignor to The Bendix Corporation, a corporation of Delaware Filed Nov. 9, 1955, Ser. No. 545,901 10 Claims. (Cl. 188 -70) This invention relates to a friction device wherein laterally applied friction elements are directly applied by the operator and develop necessary applying force for an arcuate shoe lfriction element which is radially applied. The present invention is related to co-pending application No. 482,827, filed January '19, 1955, now Patent No. 2,910,144. The present invention and the invention shown in the cited application are related in that the arcuate shoe is de-energizing during forward applica- ,tion so that it acts as a trailing shoe brake. The purpose in providing a trailing shoe brake is to minimize perfomance variations owing to change in brake effectiveness during brake application.

One of the objects of the invention is to provide an applying linkage between the disk and arcuate shoe elements through which applying effort is exerted on the Iarcuate shoe friction element during braking in both directions.

A further object of the invention is to provide a camming arrangement which develops applying thrust on an arcuate shoe friction element in a braking system having both disk and arcuate shoes which are independent- 1y pivoted in the brake.

A further object of the invention is to utilize a camming arrangement in conjunction with an applying linkage so that the torque reaction from disk brake elements may exert any preferred applying effort on the shoe friction element through said applying linkage.

An important part of the present invention is 'that the applying linkage is freely oatable to ensure that applying effort on the arcuate shoe remains proportionate to circumferential movement of the disk elements.

A very significant feature of the invention is that of providing a camniing arrangement wherein but a single cam is required to apply the arcuate friction element, this result being obtained by contouring a cammed surface in which diiferent faces of t-he cammed surfaces are engaged depending upon the vdirection of movement of the applying linkage.

A further feature of the invention is that the applying linkage not only develops applying force lfor the arcuate friction element but also can be used to apply a second arcuate friction element.

An over-all object of the invention is to improve brake effectiveness by increasing applying eort on the arcuate shoe friction element through camming devices.

The above and other objects and features of the invention will appear more fully hereinafter from a consideration of the following description, taken in connection with the accompanying drawings wherein a plurality of embodiments of the invention are illustrated by way of example. In the drawings:

Figure l is a side elevation of a brake assembly constituting a first embodiment of the invention. A part of the rotor is removed so that the brake assembly may be better viewed;

Figures 2, 3, and-4 are section views taken respectively on the lines 2 2, 3 3, and 4*4 of Figure V1;

Figure 5 is a side elevation of a second embodiment of the invention with a part `of .the rotor removed; and

Figure 6 is a side elevation of a yet further embodiment of the invention.

Referring to lthe embodiment shown in Figures 1 to 4, a stationary torque-taking plate 12 is secured VVto a xed part of the vehicle such as an axle ilange (not shown) Patented Aug. 30, 1960 f,ce

by means of bolts or the like 14. Two oppositely acting disk friction elements 16 are laterally applied by articulated levers 18 in the manner described in co-pending application No. 433,609, filed lune 1, 1954, now Patent No. 2,927,664. An arcuate shoe friction element 20 is pivoted at one end on an Ianchor 22 which is received in the torque-taking member `12.

The arcuate shoe 20 consists of a rim 24 having friction material lining 26 and a transverse strengthening web 28. Between the disk `and arcuate shoe there is a bell crank 30 which is secured to the torque-taking member 12 through a pivot post 32 which permits swinging of the bell crank about the post in either clockwise or counterclockwise direction. The bell crank is joined with the disk and arcuate shoe elements at the other two ends through camming devices 3'4 and 36, respectively. The camming devices 34 may, if desired, be constructed similarly to the ones shown in co-pending application No. 486,184, iiled February 4, 1955, now Patent No. 2,849,- 088. Cam 36 (Figures 1 and 4) consists of a roller 38 which lits into a notch 40 in the end of the web 28 of the brake shoe.

The sides of the notch are cam surfaces 45 and 47 which are engaged by the roller 38.

The pin 39 which is usedA to journal the roller 38 is carried at opposite sides by two stampings 44 and 46 which are spaced apart sufficiently to receive the roller 38 therebetween (Figure 4). The stampings 44 and 46 are attached at one end to a bushing 48 which receives the self energizing cams 3'4 so that circumferential movement of the disk elements causes turning or swinging movement of the bell crank about post 32.

Two return springs 50 (Figures l and 4) are attached between opposite ends of post 39 and opposite ends of a second upright member 52 which is located in the web 28 of the arcuate brake shoe 29. The return springs 50 are located on opposite sides of the web so that no offset lateral load is exerted on the arcuate shoe. The tension in the springs 50 causes the roller 38 to bottom inthe notch 40, thus causing turning of the shoe to disengage lining 26 from frictional engagement with the rotor 41.

Assuming forward rotation of the vehicle, the rotor 41 (fully described and claimed in co-pending application No. 434,846, filed .lune 7, 1954), now abandoned is turning in a'counterclockwise direction (Figure l). When the operator develops applying force through a pedal or the like, iiuid motor 54 operates the articulate levers 18 to spread the disk elements 16 apart bringing the friction material lining thereon into forcible engagement with the spaced sides of the rotor. The engagement of the disk friction elements with these spaced sides of the rotor produces a tendency for the disk elements to shift with the rotor in a counterclockwise direction owing to the wiping action between the friction surfaces of the disk elements and the sides of the rotor with which they are engaged. As the disk elements shift in a counterclockwise direction, the bell crank30 is caused to swing in a counterclockwise direction about post 32. This turning of the bell crank causes the cam 38 to mount side 45 of the camming surface formed at the end of the web 28. The cam 38, while climbing the cam surface 45, exerts a radial force on the shoe 20 causing it to turn on the anchor pin 22. As the shoe is turned on the anchor pin 22, the friction material lining 26 is brought into forcible engagement with the cylindrical surface of the rotor. The bell crank 30 is held against further turning on post 32 when the shoe 20 Vis fully engaged. Any further circumferential shifting of the Ydisk elements 16 is relative to the bell crank 30 so lthat the camming devices 34 will .then exert lateral spreading force onthe disk elements.

iWhen the brake isl released,1a' suitable return spring Y v43v (Figure 3) isV provided between thedisk-elements for releasing them from engagement with the rotor. The springs Si) then rotate both 'the bell crank 30 and the shoe f'20untill-th'e' cam 38 is returned to the nadir of theV Anotch 4t). The-arcuate shoe 20, being'thuspivoted in the'inanner described, is retracted from engagement -with 'the cylindrical surface of the rotor. Y Y

l #In reverse vehicle movement the rotor turnsA clockwise and: the' engagementf'of disk elements 16 withv the Vrotor produces a tendency-of the idislc'elernentsV to shift with "the rotor in a clockwiserrdirection. The disk elementsY disengaged andthe shoe is pivoted to retracted posif Ytion' :byVV the springs 50, the --bell crank being pivoted in acounterclockwis'e direction during retraction ofthe arcuate shoe. It 'will be noted` that Vthe arcuate'shoe is energizing during brake application'inthis direction of rotor movement. Y Y Y Y Y Referring next to the'embodiment shown in Figure 5,

'Y parts of the brake assembly corresponding to those -pre- Y viouisly described willreceive the same reference nu- -meral with the subscript a. Disk elements 16a which `areactuated by articulated levers 18a are connected with la floatable bell crank 30a which is fastened Yat one end 1 -with'the disk'element16a through cams 34a and at the Y other end bears against cam surfaces 45a or 47a through f Ya roller cam 38a. The arcuate'V shoe 20a Yhasra rim 24a with friction Ymaterial lining 26a and a transverse strengthening web 28a which is'mounted on an anchor fZZa'rfiXedly secured to torqueftakiug plate 12a. i Y

/Thefo positionY ofthe bell crank iiari'sk determined eby the location of a cam 56 with respect to a notch 57Y that*` is formed in the torque-takingY memberV 121i. 'A

' 'second friction element 58 isY associated Iwith disk eleme'nts16a. The friction'element 58 comprises a rim 60 having friction material lining 62 ina mounting segfY inenty64 which is joined to the .disk elements in Yshoe 20a is r'etr'actedrfrom the cylindrical surface of the rotor by turningjthe bell crank to its original position and rotating the arcuate shoe. Y

During braking in the opposite direction of vehicle movement, the rotor turns clockwise and the disk elements are causedfto .shift'therewith'in a clockwise di- ;r'ection when*thenei'fice'V is initiallyY operated. t TheoatableV bell crank S'ilf isV turned-.in fa clockwisejidirection 'Y t with the roller camlSSa mounting side47'a to apply the arcuate shoe 20a. y y Y Y When the shoeris fully applied, thercam y56 mounts side'i as the diskY elements 16a continue to shift in a clockwise direction. It YwillQbe'noted. that thefulcrum ofthelibell crank 30a changes from cam 56 to the cylin- Vdrical Vcam Y38a after the arcuate shoe 20aV is fullyapplied Aand can pivot 'no further onanchor 22a. vThe bell'crank thus exerts applying forceA on'. friction element 58.V

When the brakeis released, each of the friction velements is retracted in the .same manner as in the previous embodiment. i

Considering next the embodiment shown in Figure 6,

Yparts'ofrthe VVbrake corresponding to those previously describedwill Vreceive thesame referenceV numeral with the subscriptV b attached thereto. The "disk elements 16b' are actuated byV articulated leversx18b .when the operator 'actuates the device; i The disk friction elements 16b are attached Yto a `second Yfriction element V2Gb through a cam arrangement 3417.V Friction elementllb consists of a rim 24b having' friction materialrlining 26b and a Ystrengthening 'web 28b.j Roller cams 38b are mounted at the inner portion off the web to the friction element 20h. The roller cams are cooperable with camming surfaces S7b' which are contoured in torque-taking member 12b. In operation, the disk elements are ini- .tially spread apart toengage the sides' of the rotor.

The wiping action between the -disklelemcnts and the rotor produces Va tendency YVof the Vdiskelementsfto. shift Y with the rotor. in the saine direction. Assuming forward movementV of the vehicle during brakinggthe rotor 41b is turning in a'countercloc'k'tvisev direction .causing the 'Y disk' elementsV to move therewith (Figure 6). The disk suitable manner such as, for eXample,"by journal pin or the like 66. Y Y. Y Y' When the device is operated, the disk elements 16a are initially brought into engagement with the sides of the rotor justas Yin the prior ern-bodiment.-V Assuming forward vehicleY movement with counterclockwise rota? t Y tion of the rotor, the disk elements te'nd to move withV n therotor in a counterclockwise` directionowing tothe wiping Vaction between the 'disk elementsA and the engagel able sides of the rotor.

' the disk elements causes the floatablebell crank 30ato -turn counterclookwise on trunnion 68.

Rotation of the bell crank c ausesV the roller cam 38a `to mountside 45a ofthe camming surface formed in Y A the Web`28a at Ythe end of the arcuatershroe 20a,

" VWhen the arcuate shoe is fully applied, no further movement of' the bell crank is permitted. It will be understood'that Yall turningV of the -bell crank 30d is pro-V ducible by the wiping action between the disk elements Y andthe sides of the rotor. Y When the device is fully` ap-Y plied, the disk elements are in engagement withthe spaced Vsidesrof Vthe rotorjandthe arcuate 'friction element 20a is in engagement Vwith thecylindricalsurf-ace Vof the rotor.V Y Y Y 'When the brakelis released, the disk elements are're-VV 4turned in' any suitable manner.V The bell? crank 30a Vis returnedy to its Yoriginal position soA that the'cam 56 conj tacts the-lowermost Ypart.V of the notch`57. The VYbrake Counterclockwise movement of elements, being joined Vto the' friction element' 2Gb through the'camming devices'34b also cause the latter to shift in a counterclockwise direction. i When the friction element 20h moves counterclockwise, the Yroller cams -38b rare caused to mount camming surfaces S7b thus biasing Vthe device in a radial direction Vto apply the Vfriction material lining 26b against the cylindrical :sur-

' facerof the rotor 41b.

When the friction element 20'b is held againstfurther circumferential movement, any further movement of the disk element relatively thereto, produces additional lateral spreading force on the Vdisk elements as developed bycams34b,Y VV@ ,Y

During'rev'erse vehicle movement with clockwise ro- Vtation ofthe rotor, engagement'. of the 'disk elements produces a clockwise shifting. therewith. The friction element 20h is also caused to movein a clockwise `di rection owing to the connection ofthe Ydisk elements therewithV through the cams Y34b.Y The rollers 38b are Vthen caused to 'mount the sides of the camming surfaces S7b so that the 'friction element is biased ina radial direction causing lining 26h to engage the cylindrical surface` of the rotor. When the friction element 2Gb is held against further circumferential movemenn, the cams 34b exert additional spreading forceY on 'the'r disk ele ments 1Gb if the latter should' continue to move in a `circumferential sense'. Y v f Y ItV willV be understood from a conx'derationr of the operation of the device',lthat arcuate s'hoebraking is obtained in either direction of: vehicle movement. When the `brake is released,V any suitable return spring'eirpedient may be used to return the various; elements `to1their initial or retracted position. Y

-From a consideration of the foregoing description it will be apparent that the principles of the invention are susceptible of numerous applications. The example embodiments are illustrative of the invention and are not intended to be restrictive thereof. It will be understood that the numerous adaptations of the invention which embody the principles thereof are intended to be included within the scope of the following claims.

I claim:

1. A kinetic-energy-absorbing device comprising an arcuate friction element which is mounted for pivotal movement, a pair of disk brake elements which are movable in opposite directions along a line parallel to the pivotal axis of said arcuate friction element and which are shiftable in a plane perpendicular to their direction of movement, a bell crank pivotally secured to a fixed member, means for securing one end of said bell crank to the disk brake elements so that shiftable movement of said brake elements produces turning of said bell crank, and cam means located between the other end of said bell crank and the applied end of said arcuate friction element, said cammed means including cam surfaces formed on the applied end of said arcuate friction element so that turning of said bell crank imparts applying thrust on said arcuate friction element.

2. A friction device comprising a pair of disk elements which 'are initially spread apart in operating the device, an arcuate friction element having a lined rim, anchoring means associated with one end of said arcuate friction element and providing a pivot therefor, a stationary torque-taking means, and biasing means mounted for swinging movement on said torque-taking means and connecting said disk and arcuate friction elements, a first camming means joining said disk elements and said biasing means and arranged to spread apart said disk elements and a second camming means between said biasing means and arcuate friction element which develops thrust on said arcuate friction element responsively to turning of the biasing means.

3. A friction device in combination with a U-shaped cross section rotor comprising two separately pivoted frietion units, one of said units including a pair of disk brake elements which are laterally actuated along a line parallel to the pivotal axis of rotation of the unit, the other of said units including an arcuate friction element which is radially actuated, a torque-taking means, and an applying means joining said disk and arcuate friction elements, said applying means including cams which assist in moving apart said disk elements and a pivot for said applying means on said stationary torque-taking means about which said applying means turns to thereby exert applying force on the arcuate friction element, said applying means being further arranged to pivot on said arcuate friction element to produce radial applying thrust on a portion of said arcuate brake element to engage said portion with a cylindrical side of said rotor.

4. A friction device comprising two separately pivoted friction units, one of said units comprising oppositely applied disk elements movable apart along a line parallel to the pivotal axis of the unit, applying means operatively secured to said disk elements while providing for pivotal movement thereof, torque-taking means arranged to pivot said applying means, the other of said units comprising a principal arcuate shoe adapted for radial application by said applying means when the applying means is pivoted in either direction and a secondary arcuate shoe which is applied by said `applying means during braking in one direction only as said applying means pivots on said primary shoe, and means interconnecting said units -to translate pivotal movement of said disk elements to applying effort on said shoe element, said last mentioned means including cams which assist in moving apart said disk elements and further transmitting applying force to said principal and secondary arcuate shoes.

5. A friction device including two friction elements which are movable in opposite directions along a common axis and which are constructed with at sector shaped friction surfaces, said elements also being shiftable in a plane perpendicular to their axis of movement, means for constraining shifting of the friction elements, an arcuate friction element which is pivoted independently of said oppositely-acting friction elements, means for both pivoting and anchoring said arcuate friction element, force-transmitting turnable cam means interconnecting said oppositely-acting friction elements and arcuate friction element to develop applying force on the arcuate friction element responsively to shifting of said oppositely-acting friction elements.

6. A friction device according to claim 5 including a bell crank having a camming connection with said arcuate friction element and a camming connection with said oppositely-acting friction elements.

7. A friction device according to`claim 6 in which the camming device associated with the arcuate friction element consists of a camming roller carried by the bell crank and a notched cam profile constructed on said arcuate friction element so that turning of the bell crank in either direction will produce radially outward movement of the arcuate friction element.

84 In a friction fdevice, the combination of two separately pivoted friction units, one of said units comprising a pair of disk members which are movable apart along a line parallel to the pivotal axis of the unit, the other of said units including an arcuate shoe element, means for moving apart said disk elements while providing for pivotal movement thereof, and means interconnecting said units to translate pivotal movement of said disk elements to applying effort on said shoe element, said last mentioned means including cams which assist in moving apart said disk elements and funther transmit applying force to said shoe element.

9. In a friction device having a support member, the combination of an arcuate friction element mounted on said support member for limited pivotal movement, disk friction elements which are movable in opposite directions along a line parallel to the pivotal axis of said arcuate friction element and shiftable in a plane perpendicular to said line of movement, means for mounting said disk elements to be in end-to-end relation with said arcuate friction element, means connecting said disk and arcuate friction elements to translate shifting of said disk elements to applying force on said arcaute element, and iloatable camming means including a camming member carried by said connecting means and a cam follower formed integrally with the adjacent end of said arcuate' friction element to exert applying force on said arcuate element responsively to shifting of said disk elements in either direction.

10. A brake structure in accordance with claim 8 wherein said means for interconnecting said units includes a oatable lever, Ia cam and a cam surface which is so contoured that radially directed applying force on the shoe is developed through said oatable lever in either direction of turning of said lever.

References Cited in the le of this patent UNITED STATES PATENTS 1,603,963 Lebowitz Oct. 19, 1926 1,838,131 Bendix et al Dec. 29, 1931 1,925,897 Fawick Sept. 5, 1933 2,065,382 Levy Dec. 22, 1936 2,070,470 Clench Feb. 9, 1937 2,355,827 Stelzer Aug. 15, 1944 2,602,525 Jurgens `Iuly 8, 1952 2,751,046 Tack June 19, 1956 2,849,088 Burnett Aug. 26, 1958 FOREIGN PATENTS 457,483 nary Mar. 2o, 195o 

